US8632323B2 - Internal gear pump rotor, and internal gear pump using the rotor - Google Patents

Internal gear pump rotor, and internal gear pump using the rotor Download PDF

Info

Publication number
US8632323B2
US8632323B2 US12/682,025 US68202509A US8632323B2 US 8632323 B2 US8632323 B2 US 8632323B2 US 68202509 A US68202509 A US 68202509A US 8632323 B2 US8632323 B2 US 8632323B2
Authority
US
United States
Prior art keywords
rotor
inner rotor
formation
addendum
circle
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active, expires
Application number
US12/682,025
Other languages
English (en)
Other versions
US20100209276A1 (en
Inventor
Masato Uozumi
Harumitsu Sasaki
Kentaro Yoshida
Yuichirou Egami
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Sumitomo Electric Sintered Alloy Ltd
Original Assignee
Sumitomo Electric Sintered Alloy Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Sumitomo Electric Sintered Alloy Ltd filed Critical Sumitomo Electric Sintered Alloy Ltd
Assigned to SUMITOMO ELECTRIC SINTERED ALLOY, LTD. reassignment SUMITOMO ELECTRIC SINTERED ALLOY, LTD. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: EGAMI, YUICHIROU, SASAKI, HARUMITSU, YOSHIDA, KENTARO, UOZUMI, MASATO
Publication of US20100209276A1 publication Critical patent/US20100209276A1/en
Application granted granted Critical
Publication of US8632323B2 publication Critical patent/US8632323B2/en
Active legal-status Critical Current
Adjusted expiration legal-status Critical

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/082—Details specially related to intermeshing engagement type machines or pumps
    • F04C2/084—Toothed wheels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F04C2/102—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member the two members rotating simultaneously around their respective axes
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/19—Gearing
    • Y10T74/19949—Teeth
    • Y10T74/19963—Spur
    • Y10T74/19972—Spur form

Definitions

  • the present invention relates to an internal gear pump rotor including in combination an inner rotor and an outer rotor whose numbers of teeth are different by one, and to an internal gear pump using the rotor. More specifically, the present invention can increase the theoretical discharge amount of the pump by allowing flexibility in setting the depth and number of teeth.
  • a tooth profile of an inner rotor is formed by a base circle, a locus of one point on the circumference of an externally rolling circle that does not slip, but rolls on the base circle while being circumscribed about the base circle, and a locus of one point on the circumference of an internally rolling circle that does not slip, but rolls on the base circle while being inscribed in the base circle.
  • one base circle E, one rolling circle F, one locus circle G, and one amount of eccentricity e are set. While it is only necessary to increase the tooth depth in order to increase the discharge amount of a pump having the tooth profile, when the amount of eccentricity e between the inner rotor and an outer rotor is increased to increase the tooth depth, the tooth width becomes too small or it becomes impossible to design the tooth profile. Therefore, the amount of eccentricity e is restricted, and the tooth depth is limited. For this reason, it is difficult to meet the demand to increase the discharge amount.
  • the discharge amount can be increased by increasing the number of teeth.
  • the number of teeth increases, the radial dimension of the rotor increases.
  • the number of teeth of the rotor is determined by the diameter of a base circle and the diameters of an externally rolling circle and an internally rolling circle which form the tooth profile by rolling on the base circle without slipping thereon. Further, since the tooth depth of the rotor is determined by the diameters of the externally rolling circle and the internally rolling circle, the discharge amount of the pump depends on the diameters of the base circle and the rolling circles. For this reason, the degree of flexibility in setting the tooth depth and the number of teeth is low, and it is difficult to meet the demand to increase the discharge amount of the pump.
  • An object of the present invention is to increase the discharge amount of a pump and to suppress discharge pulsation by allowing flexibility in setting the tooth depth of a pump rotor that includes in combination an inner rotor and an outer rotor whose numbers of teeth are different by one.
  • an internal gear pump rotor including an inner rotor having n-number of teeth and an outer rotor having (n+1)-number of teeth in combination is configured as follows.
  • formation circles B and C move in a manner such as to satisfy the following conditions, and at least one of an addendum curve and a dedendum curve of a tooth profile is formed by a locus curve drawn, during the movement, by one point j that coincides with a reference point J on a base circle A concentric with an inner rotor center O I and that is on the formation circles B and C.
  • the centers pa of the formation circles B and C move from moving start points Spa and Spb where the centers are positioned when the formation circles B and C are arranged so that the point j coincides with the reference point J on the base circle A, to moving end points Lpa and Lpb where the centers are positioned when the formation circles B and C are arranged so that the point j is positioned at an addendum top T T or a dedendum bottom T B .
  • the formation circles B and C rotate through an angle ⁇ at a constant angular velocity in the same direction as moving directions of the circles.
  • the formation circles B and C two circles, that is, a circle whose center moves from the moving start point to the moving end point while keeping its diameter Bd or Cd fixed, and a circle whose center moves from the moving start point to the moving end point while decreasing its diameter Bd or Cd, are conceivable.
  • An appropriate one of the formation circles can be selected in consideration of the required performance of the pump.
  • the centers pa of the formation circles move on curves AC I and AC 2 where a change rate of the distances between the inner rotor center O I and the centers of formation circles is 0 at the moving end points Lpa and Lpb.
  • the curves AC 1 and AC 2 are curves using a sine function.
  • an addendum top T T is set on a straight line L 2 turned by an angle ⁇ T from the straight line L 1
  • a dedendum bottom T B is set on a straight line L 3 turned by an angle ⁇ B from the straight line L 1 .
  • the angle ⁇ T between the straight line L 1 and the straight line L 2 and the angle ⁇ B between the straight line L 1 and the straight line L 3 are set in consideration of, for example, the number of teeth and the ratio of setting areas of an addendum and a dedendum.
  • the moving start point Spa of the center of the addendum formation circle B and the moving start point Spb of the center of the dedendum formation circle C are on the straight line L 1 . Further, the moving end points Lpa and Lpb thereof are on the straight lines L 2 and L 3 , respectively.
  • the present invention also provides an internal gear pump rotor including an inner rotor having the above-described tooth profile and the following outer rotor in combination.
  • a tooth profile of the outer rotor is determined by the following steps:
  • a center O I of the inner rotor makes one revolution on a circle S centered on the center of the outer rotor and having a diameter (2e+t).
  • the inner rotor makes a 1/n rotation.
  • the tip clearance is defined as follows:
  • the outer rotor is set in a state in which the center of the outer rotor is at one point on the Y-axis at a distance, which is equal to the amount of eccentricity e, from the origin and an addendum top of the outer rotor meets the addendum top of the inner rotor in the negative area on the Y-axis.
  • the outer rotor center is moved on the Y-axis away from the inner rotor center until the tooth profile of the inner rotor and the tooth profile of the outer rotor come into contact with each other.
  • a clearance formed between the addendum top of the inner rotor on the Y-axis and the addendum top of the outer rotor on the Y-axis serves as the tip clearance t.
  • diameters Bd max and Cd max of the formation circles at the moving start points are set in consideration of the target tooth depth.
  • Appropriate diameters of the formation circles B and C at the moving end points Lpa and Lpb are more than or equal to 0.2 times the diameters at the moving start points Spa and Spb and less than or equal to the diameters at the moving start points Spa and Spb.
  • a tooth profile using a cycloidal curve is drawn by a locus of one point on each of an internally rolling circle and an externally rolling circle with a fixed diameter that roll on a base circle having a fixed diameter.
  • the internally rolling circle and the externally rolling circle each must move around the base circle when making the same number of rotations as the number of teeth.
  • the shape of the rotor is determined by the diameter of the base circle, the diameters of the rolling circles, and the number of teeth. Since the tooth depth is determined by the diameters of the rolling circles for themselves, there is no flexibility in changing the tooth depth. This also applies to a tooth profile formed using a trochoidal curve.
  • the tooth depth can be arbitrarily changed by changing a distance difference between R 0 and R 1 and a distance difference between r 0 and r 1 , that is, the radial moving distances R of the addendum and dedendum formation circles.
  • the tooth depth can be freely increased by setting the radial moving distances R at zero or more.
  • the increase in tooth depth increases the capacity of a pump chamber defined between the teeth of the inner rotor and the outer rotor, and thereby increases the discharge amount of the pump.
  • the tooth profiles of the addendum and the dedendum of the inner rotor are formed using the formation circles that move while changing their diameters, they can be changed by changing the change amounts of diameter from the moving start points to the moving end points of the formation circles. Hence, the degree of flexibility in designing the tooth profile increases further.
  • the tooth depth which is the sum of diameters of the internally rolling circle and the externally rolling circle, is double the amount of eccentricity between the inner rotor and the outer rotor (hereinafter simply referred to as the amount of eccentricity).
  • the internally rolling circle and the externally rolling circle each must move around the base circle when making the same number of rotations as the number of teeth.
  • the diameter of the base circle and the amount of eccentricity are determined, the number of teeth is also determined. For this reason, there is no flexibility in designing the number of teeth when the rotor size is not changed. This also applies to a tooth profile formed using a trochoidal curve.
  • FIG. 2 is an explanatory view showing a method for forming a tooth profile of an inner rotor using formation circles having a fixed diameter.
  • FIG. 3 is an image view showing a moving state of the center of an addendum formation circle having a fixed diameter.
  • FIG. 4 is an explanatory view showing a method for forming a tooth profile of an inner rotor using formation circles whose diameters change.
  • FIG. 5 is an image view showing a moving state of the center of an addendum formation circle whose diameter changes.
  • FIG. 6( a ) is an end face view of a pump rotor according to another embodiment of the present invention (addendums of an inner rotor are formed using an addendum formation circle having a fixed diameter), and FIG. 6( b ) is an end face view showing a state in which a pump chamber of the rotor is enclosed.
  • FIG. 7( a ) is an end face view of a pump rotor according to a further embodiment of the present invention (addendums of an inner rotor are formed using an addendum formation circle having a fixed diameter), and FIG. 7( b ) is an end face view showing a state in which a pump chamber of the rotor is enclosed.
  • FIG. 8 is an end face view of an example of a pump rotor in which addendums of an inner rotor are formed using a formation circle whose diameter changes.
  • FIG. 9 is a view showing a method for forming a tooth profile of an outer rotor.
  • FIG. 10 is an end face view of an internal gear pump that adopts the pump rotor shown in FIG. 1 , from which a cover of a housing is removed.
  • FIG. 11 is a view showing a tooth profile of a pump rotor of a first invention used in an example.
  • FIG. 12 is a view showing a tooth profile of a pump rotor of a second invention used in an example.
  • FIG. 13 is a view showing a tooth profile of a pump rotor of a third invention used in an example.
  • FIG. 14 is a view showing a tooth profile of a pump rotor of a fourth invention used in an example.
  • FIG. 15 is an explanatory view showing a method for forming a tooth profile using a trochoidal curve.
  • FIG. 16 is an end face view of a conventional rotor in which a trochoidal curve is used for a tooth profile of an inner rotor.
  • FIG. 17 is a view showing a tooth profile defined by a cycloidal curve in a pump rotor of a first comparative example used in an example.
  • a pump rotor according to an embodiment of the present invention will be described below with reference to FIGS. 1 to 14 attached.
  • Reference numeral 2 a denotes an addendum of the inner rotor 2
  • 2 b denotes a dedendum of the inner rotor 2 .
  • the inner rotor 2 has a shaft hole 2 c in its center.
  • a tooth profile of the inner rotor 2 is formed using a base circle A that is concentric with the inner rotor, and a formation circle B and/or a dedendum formation circle C having a point j that is provided on the circumference thereof and passes through a reference point J serving as an intersection of the base circle A and the Y-axis.
  • the base circle A is a circle having a radius extending from the inner rotor center to a boundary point between the addendum and the dedendum, and the point j starts to move from a position on the circle.
  • L 1 represents a straight line connecting the inner rotor center O I and the reference point J
  • L 2 represents a straight line connecting the inner rotor center O I to an addendum top T T
  • ⁇ T represents an angle ⁇ SpaO I T T formed by three points, namely, a moving start point Spa of the center of the addendum formation circle B, the inner rotor center of O I , and the addendum top T T (a rotation angle from the straight line L 1 to L 2 ).
  • the center pa of the addendum formation circle B moves toward the straight line L 2 through the angle ⁇ T from the moving start point Spa (this is a center position of the addendum formation circle B at a position where the point j coincides with the reference point J, and the moving start point Spa is on the straight line L 1 in FIG. 2 ) to a moving end point Lpa (this is on the straight line L 2 ).
  • the circumferential angular velocity of the center pa of the addendum formation circle B is fixed.
  • the center pa of the addendum formation circle B moves by a distance R in the radial direction of the base circle A.
  • the addendum formation circle B rotates through an angle ⁇ and the point j on the formation circle moves from the reference point J to the addendum top T T .
  • the formation circle travels ⁇ T and a distance R from the inner rotor center O I the formation circle turns 1 ⁇ 2 rotation or 180° along ⁇ which defines the point j on the dedendum or addendum curves.
  • a locus of the point j moved during this half of a tooth profile of the addendum 2 a of the inner rotor is drawn (also see FIG. 3 ).
  • the rotating direction of the addendum formation circle B is the same as the moving direction of the angle ⁇ T . That is, when the rotating direction is right-handed, the moving direction of the addendum formation circle B is also right-handed.
  • a dedendum curve can be drawn similarly.
  • a center pa of the dedendum formation circle C having a diameter Cd is moved from a moving start point Spb toward a moving end point Lpb through an angle ⁇ B while causing the dedendum formation circle C to rotate at a constant angular velocity in a direction opposite the rotating direction of the addendum formation circle B.
  • ⁇ B + ⁇ T is defined by 360°/2n.
  • the addendum formation circle B and the dedendum formation circle C move from the moving start points to the moving end points while keeping their diameters Bd and Cd constant, and half of the tooth profile of the addendum 2 a of the inner rotor is drawn by the locus of the point j formed during movement.
  • the tooth profile forming method is not limited to these methods.
  • the object of the present invention is also achieved by a method in which the addendum formation circle B and the dedendum formation circle C move from the moving start points to the moving end points while changing their diameters, and halves of the tooth profiles of the addendum and dedendum of the inner rotor are drawn by the loci of the points j formed during movement.
  • FIGS. 4 and 5 show the principle of formation of the tooth profile using formation circles whose diameters change.
  • Bd max represents the diameter of the addendum formation circle B at the moving start point
  • L 1 represents a straight line connecting the inner rotor center O I and the reference point J
  • L 2 represents a straight line connecting the inner rotor center O I and the addendum top T T
  • ⁇ T represents an angle ⁇ SpaO I T T formed by three points, namely, the moving start point Spa of the center of the addendum formation circle B, the inner rotor center O I , and the addendum top T B (a rotation angle from the straight line L 1 to L 2 ).
  • the center pa of the addendum formation circle B moves toward the straight line L 2 through the rotation angle ⁇ T from the moving start point Spa to the moving end point (this is on the straight line L 2 ).
  • the circumferential angular velocity of the center pa of the addendum formation circle B is fixed.
  • the radius of curvature of the addendum can be made larger than in the tooth profile drawn using a formation circle having a fixed diameter. Further, it is possible to obtain a tooth profile in which the difference between the clearance near the tip clearance and the tip clearance is reduced.
  • the rotating direction and the moving direction through the angle ⁇ T of the addendum formation circle B are made equal, and the tooth profile that is symmetric with respect to the straight line L 2 is formed by inverting the half of the tooth profile, which is drawn by the above-described method, with respect to the straight line L 2 .
  • a dedendum curve can be drawn similarly.
  • a dedendum formation circle C having a diameter Cd at a moving start point Spb is caused to rotate at a constant angular velocity in a direction opposite in the rotating direction of the addendum formation circle B, and is moved through an angle ⁇ B from the moving start point Spb toward a moving end point Lpb while decreasing its diameter.
  • Half of a tooth profile of a dedendum of the inner rotor is drawn by a locus formed while one point j on the circumference of the dedendum formation circle C moves from the reference point J to a dedendum bottom T B set on the straight line L 3 (this is at a position where a preset dedendum circle having a diameter D B intersects the straight line L 3 ).
  • a dedendum shape for one tooth can be obtained.
  • the change rate of the diameter of the addendum formation circle B is preferably zero at the moving end point Lpa and Lpb of the center of the formation circle. This can easily increase the radius curvature of the addendum.
  • the number of teeth of the outer rotor 3 (the number of teeth is seven in FIG. 1 ) is larger by one than that of the inner rotor 2 .
  • a tooth profile of the outer rotor 3 is formed by the following procedure, as shown in FIG. 9 .
  • the center O I of the inner rotor 2 makes one revolution on a circle S centered on the center O O of the outer rotor 3 and having a diameter (2e+t).
  • the inner rotor 2 makes a 1/n rotation.
  • An envelope of tooth profile curves formed by the revolution and rotation of the inner rotor is drawn. The envelope thus determined serves as a tooth profile.
  • the shape of dedendums may be formed in a method similar to that for the addendums using the addendum formation circle C, or may adopt a tooth profile formed using a known trochoidal curve or a tooth profile using a cycloidal curve.
  • the shape of addendums may adopt a tooth profile formed using a trochoidal curve or a tooth profile using a cycloidal curve.
  • the tooth profile using the tooth profile curve of the present invention and the cycloidal curve in combination allows smooth engage with the outer rotor that is characteristic of the cycloidal curve, and can increase the tooth depth. The demand to increase the discharge amount is thereby satisfied.
  • the addendum height and dedendum depth of the inner rotor are determined by the value of the radial moving distance R of the addendum formation circle B and the dedendum formation circle C. Since the value of the moving distance R can be freely set in the tooth profile to which the tooth profile curve of the present invention is applied, even when one of the addendum and the dedendum has a tooth profile defined by a trochoidal curve or a cycloidal curve, the degree of flexibility in setting the tooth depth is ensured.
  • the center of the formation circle moves on the curve such that the distance from the inner rotor center to the center of the formation circle increases from the moving start end toward the moving terminal end.
  • the center of the formation angle moves on the curve such that the distance decreases.
  • the formation circle rotates.
  • the tooth profile of at least one of the addendum and the dedendum of the inner rotor 2 is formed by the locus of one point on the circumference of the formation circle.
  • the tooth depth of the inner rotor can be made larger than the tooth depth in the conventional internal gear pump that adopts a tooth profile of a trochoidal curve or a tooth profile of a cycloidal curve. For this reason, the capacity of the pump chamber 4 defined between the teeth of the inner rotor 2 and the outer rotor 3 becomes larger than in the conventional pump, and this increases the discharge amount of the pump.
  • the number of teeth of the inner rotor can be made larger than the number of teeth of the conventional internal gear pump that adopts the tooth profile of a trochoidal curve or the tooth profile of a cycloidal curve. For this reason, the number of pump chambers 4 defined between the teeth of the inner rotor 2 and the outer rotor 3 becomes larger than in the conventional pump, and this increases the discharge amount of the pump.
  • the degree of flexibility in designing the tooth profile increases.
  • an addendum curve or a dedendum curve of the inner rotor is formed using the addendum formation circle or the dedendum formation circle whose diameter decreases by a fixed amount per fixed rotation angle
  • the degree of flexibility in designing the tooth profile is particularly high because the clearance near the tip clearance can be adjusted by changing the shape of the addendum.
  • FIG. 8 shows a tooth profile drawn in the method shown in FIG. 4 by increasing the change amount in distance from the inner rotor center O I to the center of the addendum formation circle B by an amount corresponding to the reduction amount of the diameter of the addendum formation circle B while reducing the diameter of the addendum formation circle B under a condition that the addendum diameter (diameter of the addendum circle) of the inner rotor 2 is fixed.
  • the radius of curvature of the addendum can be made larger and the clearance between the addendum and the adjacency of the addendum of the outer rotor can be made smaller than in the tooth profile of the inner rotor shown in FIG. 1 formed using the addendum formation circle B having the fixed diameter. For this reason, the capacity efficiency of the pump improves.
  • FIGS. 6 and 7 show pump rotors 1 according to other embodiments of the present invention.
  • An internal gear pump rotor shown in FIG. 6 is designed in a manner such that the tooth profile curve of the present invention is applied to both an addendum 2 a and a dedendum 2 b of an inner rotor 2 .
  • the tooth profile curve of the present invention is applied to an addendum 2 a of an inner rotor 2
  • a dedendum 2 b is defined by a cycloidal curve.
  • a formation circle having a fixed diameter is used to form the tooth profile curve of the present invention.
  • the internal gear pump rotor of the present invention has flexibility in designing the tooth profile even when the formation circle having the fixed diameter is used.
  • Second Invention (see FIG. 12 )
  • outer diameter of outer rotor 60 mm
  • inner diameter of inner rotor 15 mm
  • Tooth profiles were formed by the following methods.
  • a tooth profile of any outer rotor was formed by an envelope of tooth profile curves found by the method shown in FIG. 9 using the corresponding inner rotor to be combined.
  • a cycloidal curve of an addendum was formed by rolling an externally rolling circle having a diameter of 3.25 mm on a base circle having a diameter of 39 mm without slipping thereon.
  • a cycloidal curve of a dedendum was formed by rolling an internally rolling circle having a diameter of 3.25 mm on the base circle having a diameter of 39 mm without slipping thereon.
  • Addendum diameters diameters of addendum circles
  • dedendum diameters diameters of dedendum circles
  • amount of eccentricity e of the formed inner and outer rotors are as follows:
  • addendum diameter of inner rotor 45.5 mm
  • dedendum diameter of inner rotor 32.5 mm
  • addendum diameter of outer rotor 39.1 mm
  • dedendum diameter of outer rotor 52.1 mm
  • a tooth profile curve of the present invention at a dedendum was formed by the method shown in FIG. 2 using the base circle A and a formation circle C having a fixed diameter.
  • specifications are as follows:
  • dedendum diameter of outer rotor 51.9 mm
  • a tooth profile curve of the present invention at an addendum was formed by the method shown in FIG. 2 using a base circle A and a formation circle B having a fixed diameter.
  • specifications are as follows:
  • a tooth profile curve of the present invention at an addendum was formed by the method shown in FIG. 4 using a base circle A and a formation circle B whose diameter changes during movement.
  • specifications are as follows:
  • a tooth profile curve of the present invention at a dedendum of the fourth invention was formed by the method shown in FIG. 4 using the base circle A and a formation circle C whose diameter changes during movement.
  • specifications are as follows:
  • Internal gear pumps were constructed by incorporating, into the pump housing, the internal gear pump rotors formed by combining the inner rotors and the outer rotors having the above-described specifications. Then, discharge amounts of the pumps provided under the following test conditions were compared. The result of comparison is shown in the following Table I.
  • the tooth depth of the rotor and the discharge amount of the pump can be made larger than in the conventional pump in which the tooth profile of the inner rotor is formed by a trochoidal curve (see FIG. 16 ) or the conventional pump in which the tooth profile is formed by a cycloidal curve (see FIG. 17 ).
  • the diameter of the base circle and the diameters of the addendum formation circle and the dedendum formation circle can be freely set, the number of teeth can be freely set.
  • discharge pulsation of the pump can be reduced by increasing the number of teeth.
  • the discharge amount increases, compared with the comparative example. From this result, it is shown that the object of the present invention can be achieved even when the diameter of the formation circle changes during movement.
  • the pump rotor and the internal gear pump according to the present invention can be preferably used, for example, as oil pumps for lubrication of the car engine and for an automatic t transmission (AT).
  • AT automatic t transmission

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
US12/682,025 2008-08-08 2009-08-04 Internal gear pump rotor, and internal gear pump using the rotor Active 2031-08-25 US8632323B2 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP2008-205311 2008-08-08
JP2008205311 2008-08-08
PCT/JP2009/063779 WO2010016473A1 (ja) 2008-08-08 2009-08-04 内接歯車式ポンプ用ロータとそれを用いた内接歯車式ポンプ

Publications (2)

Publication Number Publication Date
US20100209276A1 US20100209276A1 (en) 2010-08-19
US8632323B2 true US8632323B2 (en) 2014-01-21

Family

ID=41663690

Family Applications (1)

Application Number Title Priority Date Filing Date
US12/682,025 Active 2031-08-25 US8632323B2 (en) 2008-08-08 2009-08-04 Internal gear pump rotor, and internal gear pump using the rotor

Country Status (7)

Country Link
US (1) US8632323B2 (ja)
EP (1) EP2206923B1 (ja)
JP (1) JP4600844B2 (ja)
KR (1) KR101107907B1 (ja)
CN (1) CN101821510B (ja)
ES (1) ES2656432T3 (ja)
WO (1) WO2010016473A1 (ja)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20140271298A1 (en) * 2011-10-24 2014-09-18 Sumitomo Electric Sintered Alloy, Ltd. Internal gear pump
US20160010739A1 (en) * 2013-03-21 2016-01-14 Voith Patent Gmbh Toothing of a gearwheel
US10180137B2 (en) 2015-11-05 2019-01-15 Ford Global Technologies, Llc Remanufacturing a transmission pump assembly
US10337509B2 (en) * 2014-10-07 2019-07-02 Toyooki Kogyo Co., Ltd. Internal gear pump

Families Citing this family (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPWO2011058908A1 (ja) * 2009-11-16 2013-03-28 住友電工焼結合金株式会社 ポンプ用ロータとそれを用いた内接歯車ポンプ
JP5194308B2 (ja) * 2010-09-29 2013-05-08 住友電工焼結合金株式会社 内接歯車式ポンプ用ロータ
JP2012137024A (ja) * 2010-12-27 2012-07-19 Sumitomo Electric Sintered Alloy Ltd 内接歯車式ポンプ用ロータ
JP5194310B2 (ja) * 2010-12-27 2013-05-08 住友電工焼結合金株式会社 内接歯車式ポンプ用ロータ
JP5765655B2 (ja) 2011-10-21 2015-08-19 住友電工焼結合金株式会社 内接歯車ポンプ
JP2013148000A (ja) 2012-01-19 2013-08-01 Sumitomo Electric Sintered Alloy Ltd 内接歯車ポンプ
JP5561287B2 (ja) * 2012-01-25 2014-07-30 住友電工焼結合金株式会社 アウターロータの歯形創成方法と内接歯車ポンプ
CN103827495B (zh) * 2012-04-17 2016-03-02 住友电工烧结合金株式会社 泵转子和使用该泵转子的内齿轮泵
CN102678829B (zh) * 2012-05-28 2014-08-20 阜新德尔汽车部件股份有限公司 液压装置用圆弧形齿廓螺旋齿轮
CN103089616B (zh) * 2013-01-28 2015-11-18 西安理工大学 一种内啮合齿廓副
CN103089963B (zh) * 2013-01-28 2015-09-30 西安理工大学 内啮合齿廓副
JP6080300B2 (ja) * 2013-03-19 2017-02-15 アイシン機工株式会社 ギヤポンプおよびインナーロータの製造方法
JP6080635B2 (ja) * 2013-03-19 2017-02-15 アイシン機工株式会社 ギヤポンプおよびインナーロータの製造方法
JP6863587B2 (ja) * 2017-08-08 2021-04-21 住友電工焼結合金株式会社 高効率内接歯車式ポンプ
KR102033258B1 (ko) 2018-10-19 2019-10-16 군산대학교산학협력단 내접기어식 펌프용 고용량 고성능 로터치형 설계방법 및 이 설계방법에 따라 제작된 로터
KR102040416B1 (ko) 2018-11-06 2019-11-04 군산대학교산학협력단 짝꿍 로터치형 생성방법 및 이 생성방법에 따라 제작된 짝꿍 로터
KR102187157B1 (ko) * 2020-02-25 2020-12-04 명화공업주식회사 내접 기어식 펌프용 로터 치형 설계방법 및 내접 기어식 펌프용 로터

Citations (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2421463A (en) * 1944-06-01 1947-06-03 Eaton Mfg Co Gear element
US2960884A (en) * 1954-11-30 1960-11-22 Hill Entpr Inc Rounded tooth tips for pointed rotoid teeth
US4350480A (en) * 1979-03-23 1982-09-21 Karl Bammert Intermeshing screw rotor machine with specific thread profile
JPS61201892A (ja) 1985-03-05 1986-09-06 Yamada Seisakusho:Kk トロコイド噛み合いする内接歯車ポンプのインナ−ロ−タ−曲線修正方法
US4657492A (en) * 1982-10-27 1987-04-14 Sumitomo Electric Industries, Ltd. Rotor for a rotary pump
US5368455A (en) * 1992-01-15 1994-11-29 Eisenmann; Siegfried A. Gear-type machine with flattened cycloidal tooth shapes
US5605518A (en) * 1993-03-26 1997-02-25 Hitachi, Ltd. Planetary gear device
US5628626A (en) * 1993-04-05 1997-05-13 Danfoss A/S Hydraulic Machine
US5772419A (en) * 1993-04-05 1998-06-30 Danfoss A/S Hydraulic machine comprising a gearwheel and annual gear having trochoid tooth sections
US6077059A (en) * 1997-04-11 2000-06-20 Mitsubishi Materials Corporation Oil pump rotor
US6101892A (en) * 1997-04-10 2000-08-15 Genesis Partners, L.P. Gear form constructions
US6244843B1 (en) * 1997-09-04 2001-06-12 Sumitomo Electric Industries, Ltd. Internal gear pump
CN1442615A (zh) 2002-03-01 2003-09-17 赫曼·海尔勒 环形齿轮机械的间隙
CN1532403A (zh) 2003-03-25 2004-09-29 ס�ѵ繤�ս�Ͻ���ʽ���� 内齿轮泵
US6902507B2 (en) * 2002-04-11 2005-06-07 Richard N. Ballard Roller cam assembly
US6929458B2 (en) * 2002-07-10 2005-08-16 Mitsubishi Materials Corporation Oil pump rotor
CN1740569A (zh) 2005-09-14 2006-03-01 中国第一汽车集团公司 变基径摆线转子机油泵
US7118359B2 (en) * 2002-07-18 2006-10-10 Mitsubishi Materials Corporation Oil pump rotor
US20060239848A1 (en) * 2002-10-29 2006-10-26 Mitsubishi Materials Corporation Internal gear type oil pump rotor
JP2007255292A (ja) 2006-03-23 2007-10-04 Sumitomo Denko Shoketsu Gokin Kk 内接歯車ポンプ
US8096795B2 (en) * 2005-09-22 2012-01-17 Aisin Seiki Kabushki Kaisha Oil pump rotor

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN1073704C (zh) * 1996-01-22 2001-10-24 华中理工大学 一种水平向拾震器
JP2006009616A (ja) * 2004-06-23 2006-01-12 Sumitomo Denko Shoketsu Gokin Kk 内接歯車式ポンプ

Patent Citations (25)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2421463A (en) * 1944-06-01 1947-06-03 Eaton Mfg Co Gear element
US2960884A (en) * 1954-11-30 1960-11-22 Hill Entpr Inc Rounded tooth tips for pointed rotoid teeth
US4350480A (en) * 1979-03-23 1982-09-21 Karl Bammert Intermeshing screw rotor machine with specific thread profile
US4657492A (en) * 1982-10-27 1987-04-14 Sumitomo Electric Industries, Ltd. Rotor for a rotary pump
JPS61201892A (ja) 1985-03-05 1986-09-06 Yamada Seisakusho:Kk トロコイド噛み合いする内接歯車ポンプのインナ−ロ−タ−曲線修正方法
US5368455A (en) * 1992-01-15 1994-11-29 Eisenmann; Siegfried A. Gear-type machine with flattened cycloidal tooth shapes
US5605518A (en) * 1993-03-26 1997-02-25 Hitachi, Ltd. Planetary gear device
US5628626A (en) * 1993-04-05 1997-05-13 Danfoss A/S Hydraulic Machine
US5772419A (en) * 1993-04-05 1998-06-30 Danfoss A/S Hydraulic machine comprising a gearwheel and annual gear having trochoid tooth sections
US6101892A (en) * 1997-04-10 2000-08-15 Genesis Partners, L.P. Gear form constructions
US6077059A (en) * 1997-04-11 2000-06-20 Mitsubishi Materials Corporation Oil pump rotor
US6244843B1 (en) * 1997-09-04 2001-06-12 Sumitomo Electric Industries, Ltd. Internal gear pump
CN1442615A (zh) 2002-03-01 2003-09-17 赫曼·海尔勒 环形齿轮机械的间隙
US20040022660A1 (en) 2002-03-01 2004-02-05 Eisenmann Siegfried A. Ring gear machine clearance
US6893238B2 (en) * 2002-03-01 2005-05-17 Siegfried A. Eisenmann Ring gear machine clearance
US6902507B2 (en) * 2002-04-11 2005-06-07 Richard N. Ballard Roller cam assembly
US6929458B2 (en) * 2002-07-10 2005-08-16 Mitsubishi Materials Corporation Oil pump rotor
US7118359B2 (en) * 2002-07-18 2006-10-10 Mitsubishi Materials Corporation Oil pump rotor
US20060239848A1 (en) * 2002-10-29 2006-10-26 Mitsubishi Materials Corporation Internal gear type oil pump rotor
CN1532403A (zh) 2003-03-25 2004-09-29 ס�ѵ繤�ս�Ͻ���ʽ���� 内齿轮泵
US20040191101A1 (en) * 2003-03-25 2004-09-30 Sumitomo Electric Sintered Alloy, Ltd. Internal gear pump
US6890164B2 (en) * 2003-03-25 2005-05-10 Sumitomo Electric Industries, Ltd. Internal gear pump
CN1740569A (zh) 2005-09-14 2006-03-01 中国第一汽车集团公司 变基径摆线转子机油泵
US8096795B2 (en) * 2005-09-22 2012-01-17 Aisin Seiki Kabushki Kaisha Oil pump rotor
JP2007255292A (ja) 2006-03-23 2007-10-04 Sumitomo Denko Shoketsu Gokin Kk 内接歯車ポンプ

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20140271298A1 (en) * 2011-10-24 2014-09-18 Sumitomo Electric Sintered Alloy, Ltd. Internal gear pump
US9541085B2 (en) * 2011-10-24 2017-01-10 Sumitomo Electric Sintered Alloy, Ltd. Internal gear pump
US20160010739A1 (en) * 2013-03-21 2016-01-14 Voith Patent Gmbh Toothing of a gearwheel
US10337509B2 (en) * 2014-10-07 2019-07-02 Toyooki Kogyo Co., Ltd. Internal gear pump
US10180137B2 (en) 2015-11-05 2019-01-15 Ford Global Technologies, Llc Remanufacturing a transmission pump assembly

Also Published As

Publication number Publication date
JPWO2010016473A1 (ja) 2012-01-26
EP2206923A4 (en) 2014-10-29
CN101821510B (zh) 2012-09-05
CN101821510A (zh) 2010-09-01
KR20100059922A (ko) 2010-06-04
KR101107907B1 (ko) 2012-01-25
US20100209276A1 (en) 2010-08-19
JP4600844B2 (ja) 2010-12-22
EP2206923A1 (en) 2010-07-14
EP2206923B1 (en) 2017-12-06
WO2010016473A1 (ja) 2010-02-11
ES2656432T3 (es) 2018-02-27

Similar Documents

Publication Publication Date Title
US8632323B2 (en) Internal gear pump rotor, and internal gear pump using the rotor
US9097250B2 (en) Pump rotor
US7407373B2 (en) Internal gear pump and an inner rotor of such a pump
US8360762B2 (en) Oil pump rotor
US8876504B2 (en) Pump rotor combining and eccentrically disposing an inner and outer rotor
KR100345406B1 (ko) 오일펌프로우터
EP2759706B1 (en) Pump rotor and internal gear pump using the same
JP6982780B2 (ja) 歯車ポンプ用ロータおよび歯車ポンプ
JP5194308B2 (ja) 内接歯車式ポンプ用ロータ
US9541085B2 (en) Internal gear pump
JP5561287B2 (ja) アウターロータの歯形創成方法と内接歯車ポンプ
JP2006009616A (ja) 内接歯車式ポンプ
JP4393943B2 (ja) オイルポンプロータ
JP2012137024A (ja) 内接歯車式ポンプ用ロータ
JP5194310B2 (ja) 内接歯車式ポンプ用ロータ
KR102033258B1 (ko) 내접기어식 펌프용 고용량 고성능 로터치형 설계방법 및 이 설계방법에 따라 제작된 로터
JP2013060924A (ja) 内接歯車ポンプ

Legal Events

Date Code Title Description
AS Assignment

Owner name: SUMITOMO ELECTRIC SINTERED ALLOY, LTD., JAPAN

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:UOZUMI, MASATO;SASAKI, HARUMITSU;YOSHIDA, KENTARO;AND OTHERS;SIGNING DATES FROM 20100310 TO 20100318;REEL/FRAME:024201/0333

STCF Information on status: patent grant

Free format text: PATENTED CASE

FEPP Fee payment procedure

Free format text: PAYOR NUMBER ASSIGNED (ORIGINAL EVENT CODE: ASPN); ENTITY STATUS OF PATENT OWNER: LARGE ENTITY

FPAY Fee payment

Year of fee payment: 4

MAFP Maintenance fee payment

Free format text: PAYMENT OF MAINTENANCE FEE, 8TH YEAR, LARGE ENTITY (ORIGINAL EVENT CODE: M1552); ENTITY STATUS OF PATENT OWNER: LARGE ENTITY

Year of fee payment: 8